Automatic transmission apparatus and controls



BANKER AUTOMATIC TRANSMISSION APPARATUS AND CONTROLS Original Filed April 24, 1940 May 9, 1950 4 Sheets-Sheet 1 4 Sheets-Sheet 2 O. H. BANKER AUTOMATIC TRANSMISSION APPARATUS AND CONTROLS May 9, T950 Original Filed April 24, 1940 4 Sheets-Sheet 15 H. BANKER UTOMTIC TRANSMISSION APPARATUS AND CONTROLS Original Filed April 24, 1940 lng- Illl'f W/////////// MN May 9, 1950 o. H. BANKE'R 2,507,137

AUTOMATIC TRANSMISSION APPARATUS AND CONTROLS Original Filed April 24, 1940 4 Sheets-Sheet 4 7 507 /fzgffzaa ,gg 65' 34' 2f? 2] 505 307@ ggg E Y 235 Patented May 9, 1950 AUTOMATIC TRANSMISSION APPARATUS AND CONTROLS Oscar H. Banker, Evanston, lll., assignor to New Products Corporation, Chicago, lll., a corporation oi' Delaware Original application April 24, 1940, Serial N0.

331,309, now Patent No. 2,394,580, dated February 12, 1946. Divided and this application April 14, 1944, Serial No. 531,130

8 Claims. (Cl. 74-336.5)

This invention has to do with change-speed apparatus for transmitting power between a throttle-controlled engine and a load, and relates particularly to such a, system employing a clutch, an automatic change-speed transmission and a fluid pressure system for controlling the operation of said clutch and said transmission according to the degree of advancement of the engine throttle and the speed of said engine. This application is a division of my copending application Serial No. 331,309, filed April 24, 1940, for Automatic transmission apparatus and controls, now issued into Patent No. 2,394,580.

A primary object of this invention is the provision of a change-speed apparatus or system satisfactorily employing a fluid motor or envelope type of clutch in the power connection between the engine and the load. Clutches comprising an inatable envelope that carries parts frictionally engageable to transmit load, when the envelope is inflated, have been used heretofore in the transmission of power, their advantages being ease of control, uniformity of action .in the application of driving force tothe load and the absorption of tortional vibrations inherent to` all reciprocating engines. However, the fiuid envelope clutch has been regarded as useful only in marine or other installationsl where speed ratio changes between the engine and load are unnecessary, or occur infrequently and without a series of shifts in rapid succession through power trains of graduated ratio as is the practice in motor vehicles. This limitation in the use of the uid envelope clutch has existed because the envelope carries one of the friction elements and would, therefore, be damaged by the heat generated in such element in prolonged severe slippage periods, when the clutch is of a size and load rating not adversely affecting its cost.

Some automotive installations employ a iiuid flywheel or uid turbine type of coupling for reducing tortional vibration. These iuid couplings, however, have the disadvantage of operating with an energy wasting slip between the driving and driven members at all speeds, of increasing the engine speed at all vehicular speeds and of causing annoying engine rush at low vehicular speeds. The present invention, as another of its objects, provides apparatus operable in a manner to obtain all of the advantages of the fluid coupling installation while avoiding said disadvantages, and this is done by combining a fluid envelope clutch with a transmission that changes speed ratio without concomitant release and reengage- 2 ment of the clutch. Inasmuch as the present type of clutch transmits power through yieldable walls of an inflated envelope, the tortional vibrations of the engine are absorbed by said walls, and, since the clutch permits no slipping between its friction elements when fully engaged, the installation accomplishes the purpose of the liuid coupling without the increment of engine speed.

A further object of the present invention is the provision of a throttle-controlled valve between a fluid pressure source and the clutch, for meting uid from the source to the clutch in an amount and at a pressure proportionate to the advancement of the engine throttle to cause the clutch to take up load slowly and uniformly as fuel is fed to the engine.

The invention further contemplates the combination of the aforesaid throttle-controlled inatable power transmission clutch in combination with a multi-ratio power transmission of the character wherein changes in the power trains are effected by closing the engine throttle for causing the engine, and transmission parts driven thereby, to slow down to synchronism' with cooperative driven parts of the transmissionassociated with a higher ratio power train and wherein means is provided for automatic/ally connecting the synchronised parts upon their synchronization for establishing such high power train. In accomplishing this object, additional valve means is provided between the uid pressure source and the clutch, and a speed-responsive device is placed in control of this additional valve means for causing the same to provide direct communication between said source and said clutch when the speed-responsive device registers engine and vehicular speeds in excess of a predetermined minimum, and to terminate the connection between the throttle-controlled valve and the clutch so that when the throttle is periodically closed during operation of the vehicle, the clutch will remain closed and fluid will not be wasted by periodic filling and exhausting thereof A further object of the invention is the provision of a new arrangement of transmission wherein the main shaft is bored axially to provide space for a tube comprising a part of the uid pressure line between the fluid pressure source and the clutch, and projects outwardly through an end of the gear box to facilitate the attachment to said tube of av coupling member communicative with an outer portion of said line.

A further object of this invention is the provi- 3 sion of a on of the countershaft type wherein the power take-oil.' is from the end of the countershaft adjacent to the clutch or bell housing and through a shaft directed substantially perpendicularly to the countershaft.

A still further object of the invention is the provision in a countershaft type transmission of an improved arrangement wherein the gears making up the low and reverse speed power trains are disposed upon central sections of said shafts and wherein the gears making up the higher ratio power trains are disposed adjacently tolte ends of said shafts and their bearing suppo Still a further object of the invention is the provision in combination with a multi-ratio,

power transmission wherein changes between the power trains are effected automatically, of means normally biased into a position for preventing establishment of the higher ratio power trains, and a fluid motor. operable to move said means into an inactive position to permit the normal automatic establishment of said power trains. said motor being so operative when subjected to uid pressure from said source under control of a valve which is operated by an engine-driven speed-responsive device when the latter registers speeds in excess of a predetermined minimum.

With the above objects in view. the preferred embodiment of the invention will now be described with reference to the annexed drawing,

wherein z Fig. 1 is a plan view, principally in section of a preferred embodiment of the invention;

Fig. 2 is a fragmentary plan view of the transmission gear box with a portion of the upper side wall of said box broken away to expose the cams and linkages for controlling the transmission power trains;

Fig. 3 is a transverse sectional view taken on the line 3-3 of Fig. 2;

Fig.4 is a longitudinal sectional view taken through a motor unit which is instrumental in controlling establishment of the second and third speed power trains;

Fig. 5 is an enlarged sectional view taken axially through the throttle-controlled valve and a foot accelerator pedal associated therewith;

Fig. 6 is a sectional view taken through a governor-controlled valve for admitting pressureuid to the main clutch of the transmission apparatus;

Fig. '1 is a sectional view taken through a governor-controlled valve which controls the admission of pressure-fluid to the fluid motor unit shown in Figs. 1, 3 and 4;

Fig. 8 is a sectional view taken through a switching valve which also appears in Fig. 1; and

Fig. 9 is an enlarged fragmentary view showing details in the connection of the fluid pressure line at the right-hand end of the transmission main shaft in Fig. 1.

Referring now to the drawing, and particularly to Fig. 1 thereof, the apparatus will be seen to include a clutch generally designated C, within a clutch housing III, a countershaft type of transmission unit generally designated T, within a gear box II, and a power take-off or driven shaft I2 extending upwardly into a chamber I3. Said shaft I2 is driven from a countershaft I4 through bevel gears i5 and I6 respectively upon the shafts I4 and I2. This drive arrangement particularly adaptsthe apparatus for use in rear engine vehicles in which the engine is mounted above the wheel I8, and has its left end section 22 carried within the flywheel-within a pilot bearing 23. Such shaft extension 20 is splined at 24 to facilitate the connection thereto of a hub 25 upon a driven member 26 of the clutch C. Snap rings 21 and 28 are employed for preventing axial movement of the clutch driven member 26 upon the shaft extension 20. Bolts 29 spaced circumferentially about the disk-like members 26 are used for securing an annular flange member` 30 thereto. Said piece 38 in turn carries an annular inflatable envelope 3| which is suitably joined thereto by a vulcanized rubber illm as indicated at 32. The envelope 3| comprises side walls of flexible fabric-reinforced rubber constructed similarly to the side walls of conventional pneumatic tire casings. A plurality of friction elements 33, in the form of axially extending bars for engagement with the clutch driving member I1, are secured to the outer periphery of the inflatable envelope 3| in any suitable manner as by means of a vulcanized rubber film 34.

When the envelope 3| is in its normal uninflated or relaxed condition its contour is such as to Withdraw the bar-like friction elements 33 from engagement with the inner periphery of the clutch driving member I1, but when said envelope is inflated with fluid under pressure the elements 33 will be forced outwardly into frictional engagement with the member I1 Whereby the clutch driven member will be caused to rotate with the driving member.

Pressure-fluid is admitted to and exhausted from the envelope 3| through a fluid pressure line comprising a tube 35, a bore 36 in the shaft extension-2|l, a tube 31 communicating with said bore 36 and extending lengthwise through the mainshaft 2| within a bore 38. A fitting 39 extends through the annular flange 3D and into communicative relation with the envelope 3| to connect the tube 35 with the envelope. A fitting 40 connects the other end of the tube 35 with a lateral passage 4| which communicates with the bore 36. The right-hand end of the bore 36, Fig. 1, is enlarged in the form of a frustro-conical flare 42 to adapt it for hermetically engaging a frustreconical exterior end section of the tube 31. A nut 43 in threaded relation with a reduced end section 43a of the mainshaft 2| has a flange 44 drawn firmly against a shoulder 45 of the tube 31 for pressing the tapered left end section of said tube firmly into the flared section 42 of the bore 36. Axial separation of the shaft 2| and the extension 20 is prevented by a coupling assembly including a nut 46 threaded upon a reduced right end section of said shaft 2| and bearing against a coupling member 41 which is splined to the shaft 2| at 48. Said coupling member 41 is also splined on its outer side at 49 as is an enlarged end section 50 of the extension shaft 20 at 5|. An internally splined ring 52 meshes with the splines 49 and 5| upon the parts 41 and 50, and snap rings 53 and 54 which are sprung outwardly into grooves cut circumferentially in the ring 52 transverselyof the spline quills bear against the ends of the spline quills 5I and 49 to prevent axial separation of the parts 41 and 50.

Pressure-fluid is introduced into the tube 31 through an L fitting 55 upon the right end of said tube, Fig- 1, and shown in detail in Fig. 9. The outlet end of the fitting 55 includes a packing gland 56 compressible by the turning of a nut 51 into an internally threaded section 58. 'Ihe inlet end of said fitting 55 has a conduit 59 in threaded relation with an internally threaded section 60 thereof, this conduit 59 connecting with the pressure-fluid system in a manner presently described.

Opposite end walls 6I and 62 of the gear box have bearing units 63 and 64 respectively disposed therein in axial alignment for rotatively supporting the mainshaft 2|. A second set of bearing units 65 and 66 Within these end walls rotatively carry the countershaft I4.

The transmission is connectible through three forward speed power trains and one reverse power train. The first speed or lowest ratio .power train receives power through the extension 20 of the mainshaft 2|, and transmits such power through a gear 61 integral with the mainshaft, a gear 68 freely rotatable about a bearing sleeve 69 upon the countershaft I4, the hub 10 of said gear 69, splines 1| upon said hub, a clutch ring 12 slidable axially of said hub 10 and having internal splines 13 meshing with the splines 1I. Said clutch ring has a plurality of circumferentially spaced axially projecting lugs 14 projecting into openings 15 respectively registered therewith in the gear 68, one of such lugs 14 and openings 15 being shown in the lower part of Fig. 1. Certain of the splines 13 upon the clutch ring 12 project onto the lugs to form clutch teeth 13', so that when the ring 12 is slid axially to the right, as viewed in Fig. 1, said teeth 13' are caused to mesh with clutch teeth 15 upon an end of a driving member 16 of an overrunning clutch 11. Said overrunning clutch driving member 16 is freely rotatable upon the hub 18 of a gear 19 which is attached nonrotatively to the countershaft I4 by a key 80. A driven element of the overrunning clutch 11 is provided by a cylindrical flange 8| which is capable of being driven by a plurality of clutch rollers 82 in one direction only as is well understood by those skilled in the art. Again picking up the drive for the rst speed power train at the clutch ring 12, when this ring is slid to the right as viewed in Fig. 1 for meshing the clutch teeth 13' with the clutch teeth 15', rotative force is transmitted to the overrunning clutch driving member 16 which is effective through the clutch rollers 82, which are wedged thereby against the inner periphery of the flange 8|, for rotating the gear 1-9 and the countershaft I4 to which said gear is non-rotatively attached. Power is transmitted outwardly of the apparatus through the ebevel gears I5 and I6 and the transmission driven shaft I2.

The second speed power train includes a clutch ring 83 splined to the mainshaft 2| and movable axially to the right for meshing clutch teeth 84 thereon with mating clutch teeth 85 upon a gear 86 which is freely rotatable upon the shaft 2|. Clutch teeth 84 and 85 have bevel end faces 81 and 88, as clearly shown in Fig. 2, so that when the clutch ring 83 is shifted to the right to press the faces 81 and 88 together while the ring 83 happens to be rotated at a greater speed than the gear 86 there will be a ratcheting action of the teeth 84 past the teeth 85 to prevent the meshing of these teeth in a manner involving no objectionable noise and incurring no injuries thereto. Similarly constructed and cooperable teeth as the clutch teeth 84 and 85 are shown and fully described in my United States Patent No. 2,140,502. The second speed power train also includes a gear 89 freely rotatable about a bearing sleeve 90 upon the countershaft I4 and in constant mesh with the gear 86. An integral sleeve 9| of the gear 89 has upon the left end thereof a driving member 92 of a second speed overrunning clutch 93. This overrunning clutch is similar to the overrunning clutch 11, the driving member 92 being effective through clutch rollers 94 for imparting rotation to a driven member 95 comprised by an annular ilange upon the gear 19. Establishment or mobilization of the second vspeed power train is accomplished by a shifter fork |04 fixed upon an operating shaft |05 therefor and having legs |08 disposed upon opposite radial sides of the ring 83 where said legs pivotly carry shoes |01 disposed within a groove |08 of the ring. Counter-clockwise pivotal movement of the shaft |05 imparts to the shoes |01 a force to cause the ring 88 to be shifted to the right for meshing the clutch teeth 84 and 85 of the second speed clutch |09. During certain periods of operation of the apparatus, when the teeth 84 and 85 of the second speed jaw clutch 96 are meshed for mobilizing the second speed -power train, power will be transmitted from the mainshaft 2| through said clutch 96, the gears 86 and 89, sleeve 9|, overrunning clutch l93, flange 95 and gear 19 to the countershaft I4 and thence outwardly of the apparatus through the gears I5 and I6 and the driven shaft I2.

During periods of operation when it is desired to hold the vehicle under close supervision, as when traveling over a rough uneven surface as those often encountered in detours, it will be desired to use the braking effect of the vehicle engine, and to accomplish this the second speed power train will be made into a two-way drive train by shunting out the `overrunning clutch 93. This is done by means of a jaw clutch 91 comprising a sildable ring member 88 internally splined at 99 to the sleeve 9|. Said ring member y98 has a groove |00 for a shifter fork IOI, Fig. 2, and a set of jaw teeth |02 meshable with a set `of jaw teeth |03 upon the gear flange 95 when the ring 98 is shifted to left as viewed in Fig. 1. When the clutch teeth |02 and |03 are thus meshed, the driving and driven ,parts of the overrunning clutch 93 are connected together for effecting a two-way drive independently of the clutch rollers 94. l

The third speed power train comprises a gear IIO freely rotatable upon the mainshaft 2| excepting when cl'utched thereto by the teeth III and II2 of a jaw clutch II3. Said teeth III of the jaw clutch II3 are integral with the gear IIO whereas the teeth II2 project axially to the left from a clutch ring |I4, which also has a groove |I5 in which are disposed shoes II5 (one of which is shown in dotted outline in Fig. 2) upon the ends oaf legs II6 of a shifter fork II'I carried non-rotatively upon a shaft IIB. When the shaft II8 is rotated clockwise the shifter fork |I1 land shoes thereon disposed within the groove II 5 of clutch ring I|4 will bear against the left side of this groove for urging the clutch teeth |I2 into mesh with the clutch teeth III. The clutch ring II4 is splined to the mainshaft 2| as indicated at II9. Also included in the 1| third speed power train is a gear |20 secured atoms? 7 non-rotatively to the countershaft |4 by a key member |2|, the gears ||0 and |20 being constantly meshed.

A reverse power train includes a mainshaft gear |30 and the countershaft gear 19. The reverse power train is established when an idler gear above the gears |30 and 19 is slid mutually into mesh with them. This idler gear is shown at |3| in Figs. 2 and 3. Referring mutually to Figs. 2 and 3, the reverse idler gear |3| will be seen to 'be carried rotatively upon a countershaft |32 of which the ends are supported in gear box brackets |33 and |34 of which both are shown in part in Fig. 2 and of which only the bracket |34 is shown in Fig. 3. The bracket |33 has a vertical leg |35 depending from the upper side wall of the gear box and a leg |36 projecting inwardly from a vertical side wall of the gear box. A junction section |31 of these legs |35 and |36 carries one end of the countershaft |32. A leg |38 of the bracket |34 depends from the upper wall of the gear box, whereas a horizontal leg |39 projects inwardly from a vertical side wall of the gear box, and a junction section |40 of these legs carries the other end of said shaft |32. It will also be noted in Fig. 3 that the bracket leg |39 provides'a bearing section |4| for one end of the shifter fork operating shaft |05. The idler gear |3| has a shifter ring |42 attached to its left end, Fig. 2, there being a groove |43 in said ring for receiving vthe bifurcations |44 of a shifter fork |45. Both bifurcations |44 of the shifter fork |45 are shown in Fig. 3 in dotted outline; one of such bifurcations is shown in Fig. 2.

A sleeve-like base section |46 of the reverse shifter fork |45 is slidably mounted upon a shifter fork rod |41 anchored in opposite ends of the gear box. A detent ball |48, shown in dotted outline in Fig. 2, is carried in the sleeve |46 where it is constantly urged by a spring |49 against the rod |41. This rod has a pair of notches |50 and in either of which the detent |48 is adapted to be seated by the spring |49 when in registry therewith. When the shifter fork |45 occupies the position shown in Fig. 2 with the detent |48 seated in the recess |5|, the reverse idler gear |3| is disposed in a position to the right of and out of mesh with the reverse train gears |30 and 19; thereby demobilizing the reverse speed power train. Shifting of the fork 45 to the left upon the rod |41, as viewed in Fig. 2, is resisted by the detent |48 as it is cammed outwardly of the notch |5| against the urge of the spring |49, but when the fork |45 is shifted sumciently far to the left to carry the idler gear |3| mutually into mesh with the gears |30 and 19 for establishing the reverse power train, the detent |48 will have reached a rposition of registry with the notch |50 to seat therein and thus yielda'bly resist demeshing of the gears.

As is explained hereinabove with reference to Fig. 1, mobilization of the lowest or first speed power train is accomplished by sliding a clutch ring 12 to the right for carrying the clutch teeth 13' thereon into mesh with the clutch teeth 15 on the driving member 16 of the first speed overrunning clutch 11. Shifting of the clutch ring 12 is accomplished by means of a shifter fork |52, Fig. 2, of which the bifurcations project into a groove |53 in said ring. This shifter fork |52 has a sleeve-like base section |54 slidably mounted upon the shifter fork rod |41 and` a detent device comprising a ball |55 shown in dotted outline in Fig. 2 within said base section |54 for cooperating with a pair of notches |56 and |51 in the rod |41 in a manner similar to that described with respect to the ball |43. A spring |53, shown in dotted outline, constantly urges the ball |55 against the rod |41. When the shifter fork |52 is in the position shown in Fig. 2, the clutch ring 12 will be held to the left demeshing the clutch teeth 13 and 15', as illustrated in Fig. 1. The detent device comprising the ball |55 yieldably resists movement of the shifter fork |52 and of the clutch ring 12 from this position, but when said fork is shifted to the right while camming the ball |55 out of the notch |56, the clutch ring 12 will be moved to the right and will completely mesh the clutch teeth 13' and 15 at the time the ball |55 is moved into seating relation with the notch |51. At this time the first speed power train will be mobilized.

Shifting of the forks |45 and |52 of the reverse power train and of the first speed power train is accomplished by means of cylindrical studs |59 and |60 projecting respectively from the sleeve-like base portions |46 and |54 of these shifter forks into cooperative relation with cam slots i6| and |62 in a cam plate |63, Figs. 2 and 3. This cam is manually controlled. It is fixed to the lower end section of a control shaft |64, which, as shown in Fig. 3, has a control arm |65 non-rotatatively secured to its upper end. A linkage (not shown) extends from the end of the control arm |65 into a position conveniently accessible to thev driver of the vehicle.

The cam plate 63, in selectively mobilizing either the first speed power train or reverse power train is rotated between oscillative limits. rIhe plate |63 is illustrated in Fig. 2 in a neutral position wherein neither of these power trains is mobilized. Mobilization of the reverse power train is effected by rotating the cam plate |63 clockwise whereby the stud |59 is cammed to the left by an edge |66 of the slot |6| to move the shifter fork |45 and the idler gear |3| to the left to carry said gear mutually into mesh with the reverse power train gears |30 and 19. At the end of this operative movement of the cam plate |63 the detent ball |48 will be seated in the notch |50. Meanwhile, the arcuate slot section |61, concentric with the axis of the shaft |64, will have simply received the stud |60 without having shifted it axially of the rod |41.

When it is later desired to demobilze the reverse power train the cam plate |63 will be r0- tated in the opposite direction, and during this rotation the edge |68 of the slot |6| will be operative for camming the stud |59 to the right into the position shown while the arcuate notch section |61 will again idly traverse the stud |60. When it is desired to mobilize the first speed power train the cam plate |63 will be rotated counter-clockwise to close the edge |69 of the slot |62 to shift the stud |60 to the right by a camming action thereon, and to thus shift the fork |52 to the right for engaging the clutch teeth 13 and 15', Fig. 1. Meanwhile, the detent ball |55 will have shifted into registry with the notch |51, and the arcuate portion |10 of the slot |6| will have simply moved idly with respect to the stud |59 without shifting it. Demobilization of the first speed power train is accomplished by rotating the cam plate |63 clockwise from the just described position while the edge 1| of the slot'l |62 is effective for camming the stud |60 to the left into the position shown in Fig. 2 and t0 thus demesh the clutch teeth 13' and 15' of the flrst speed jaw clutch.

A sleeve |16, Figs. 2 and 3, is rotatively mounted upon the control shaft |94. This sleeve projects upwardly through the upper wall of the gear box where it carries the hub |16 of an operating arm |11. The inner and lower end of the sleeve non-rotatively carries a cam plate |18 above and in parallelism with the cam plate |63 as is best illustrated in Fig. 3. Only an edge portion of the cam plate |18 is shown in Fig. 2, this cam plate being broken away at the line |19 to expose the slots |6| and |62 in the cam plate |63. The cam plate |18 is controlled by a governor |66 to prevent automatic engagement of the second and third speed clutches |09 and ||3, Figs. 1 and 2, while the vehicle is at rest or is proceeding at speeds below a predetermined minimum. This it accomplishes by means of edge profile section |80 ending at a point |8| and cam sections |82 and |83 which, through a roller |84 upon an arm |85, control the pivoted position of such arm about a pin |98 anchored in the upper wall of the gear box. Just how the arm |85 constrains engagement of the clutches |09 and |3 will be explained presently, but first it will be explained that the cam |63 is also operable upon the roller |84 for controlling the pivotal position of the arm 85 by means of edge profile sections identical to and directly beneath the cam profile sections |80, |82 and |83 and designated by the reference characters |80', |82 and |83'. These latter named cam profile sections are also indicated in Fig. 3 where the relation of the cam plates |63 and |18 with respect to the roller |84 are shown.

As previously explained, the cam plate |63 is manually controlled for determining whether the vehicle shall be driven forwardly or backwardly, or whether the transmission mechanism shall be arranged in a neutral position so the vehicle will be driven neither forwardly nor backwardly. When the plate |63 is inthe neutral position, as shown in Fig. 2, or in the reverse position, the cam point I8 or the adjacent long radius proiile section |80' of said cam plate will be in registry with the roller |84 for maintaining the 'arm |85 in the position shown and thereby prevent engagement of either oi.'l the overrunning jaw clutches |09 and ||3, as will be explained.

Referring now to Figs. 2 and 3, a coil spring |90 will be seen wrapped about the lower bearing member |92 for the control shaft |05 which carries the second speed shifter fork |04. One end, |93, of this spring reacts against a wall of the gear box, whereas the other end, |94, is hooked about the lower leg of said shifter fork |04 to constantly urge said fork to pivot in a direction for shifting the clutch teeth 84 toward the clutch teeth 85.

Also secured to the shaft |05, at its upper end, is an arm |95 pivotally connected to a link |96 by a pin |91 at its end. The opposite end of the link |95 is connected with the right end of the arm |85, Fig. 2, by a pivot pin |99. It will be seen that any tendency for the shifter fork |04 to be rotated counter-clockwise, Fig. 2, by the spring |90 will tend to cause the left end of the arm |95, as well as the link |96 and the right end of the arm |85, to move toward the cam plates |18 and |63, and when either of the cam points |8| or |8|' is in registry with the roller |84 this movement cannot take place. However, if both of the Vcaml plates |18 and |63 were to be rotated counter-clockwise to bring vtheir short radius profile sections |83 and |83' into registry with the roller |82 there would be no impediment to such movement of the arms |95 and |85 and the link |96, wherefore the action of the spring 10 |90 would result in pivotal movement of -the fork |04 for shifting the clutch teeth 84 into engagement with the clutch teeth and into mesh ilslliigrwith when these sets of teeth are synchrovA spring 200, Fig. 2, similar to the spring |90, has an end section 20| which reacts against a side wall oi the gear box and an opposite end 292 hooked about the lower leg ||6 of the shifter fork I1, `thereby constantly urging clockwise pivotal movement of said shifter fork ||1. When, however, either of the cam points |8| or |8|' is in registry with the roller |84, such clockwise rotation of the shifter fork ||1 and the shaft ||6 upon which it is mounted will be prevented by an arm 203 which is non-rotatively secured to the upper end of said shaft and of which. arm a free vend section bears against an upwardly projecting portion of the link pin |91. .f

The governor-controlled apparatus for determining the pivoted position of the cam plate |19 n includes a iluid controlled unit or motor 205 secured to the upper wall of the gear box as illustrated in Fig. 3. This motor is shown in detail in Fig. 4 where it will be seen to comprise a cylinder 206 in which there is a piston 201 which is normally held in the position shown by pressurefluid introduced into the cylinder through a conduit 208. The pressure of said uid will be such as to overcome the force of a spring 209 which surrounds an operating rod 2 0 extending through a spring chamber 2|| into connection with said piston. An adjustable clevis 2|2 interconnects the rod 2|0 and the arm |11 by means of a pivot pin 2| 3. Hence it will be seen that when pressure-fluid is present in the cylinder 208 the arm |11, the sleeve |15, Figs. 2, 3 and 4, and the cam plate |18 will be pivoted to the limit of their clockwise movement for disposing the cam point |8| against the roller |84. l When the pressurefluid in the cylinder 206 is released, the spring 209-will be eiective for expelling the iiuid from the cylinder while rotating the arm |11 and the cam plate |18 counter-clockwise to bring the short radius cam profile section |83 into registry with the roller |84 whereby the cam |18 will permit engagement of the overrunning jaw clutches |09 and ||3 oi the second and third speed power trains.

'I'he motor unit 205 is shown schematically in Fig. 1 where it will be seen that uid pressure ltherefor is received from a pressure tank or reservoir 2|4 through a conduit 2|5, a branch conduit 2|6, a valve 2|1 and the conduit 208. The valve 2|1, shown in detail in Fig. '1, normally provides communication between the reservoir 2|4 and the motor 205. When, however, this valve is actuated under control of the governor |96, it will be conditioned for terminating the communication between the reservoir and said motor and for opening an exhaust port 233 through which the pressure-fluid within the cylinder 206 is discharged pursuant to the spring 209 forcing the piston 201 to the opposite limit of its reciprocal movement.

A second valve 236, instrumental in the control of the clutch C as will be explained presently, is secured to a side wall oi the gear box. Connecting members 231 and 238 are employed for securing the valves 2|1 and 236 together in spaced apart relation so as to accommodate a,

valve actuating link 239 between said valves. The valve 236, shown in detail in Fig. 6, is controlled by a reciprocal valve stem 253 provided with a cap 240 whereas the valve 2|1 is controlled by a reciprocal valve stem 234 having a cap 235, and axial movement of these valve stems is effected by a cross-piece 24| upon the link 239 when the latter is moved to the right.

An examination of the construction details of the valve 2 I 1, in Fig. 7, shows it to have a central chamber 2|9 closed at opposite ends by plugs 220 and 22| which are screwed into place. Pressure-fluid is fed into the valve 2|1 through the conduit 2| 6, Fig. 1, which has a threaded end section connected with the valve inlet port 222. Fluid introduced to the valve at the port 222 feeds inwardly through a channel 223 in the plug 220, an axial channel 224 intersecting the channel 223, past a valve seat 225 into the valve chamber 2|9, and thence out through an outlet port 26 with which the conduit 208 is connected as illustrated in Fig. l. A spring 221 normally holds a valve head 228 away from the seat 225 for maintaining the just traced passages of the-valve open and for holding the opposite end of the valve head against a seat 229 about the entrance of an exhaust passage which comprises an axial channel 230 in the plug 22|, a transverse channel 23| in said plug, a channel 232 in the valve chamber casing, and an exhaust port 233. The valve stem 234 connects the valve head 228 with the cap 235. It will be seen that when an external force is applied to the cap 235, the stem 234 and the valve head 228 will be moved to the left,

Fig. 7, against the "yieldable force of the spring 221 for closing the above traced feed line between the inlet port 222 and the outlet port 226,-while unseating the valve head from the seat 229 and thereby connecting the outlet port 226 with the exhaust port 233 through the chamber 2|9 and the channels 230, 23| and 232.

The valve 236 has an inlet port 24'2, an outlet port 243 and an exhaust port 244. While in the valve 2|1, the inlet and outlet ports 222 and 226 are normally in communication through the valve, the converse is true with respect to the valve 236. A potential passage for the flow of fluid between the inlet port 242 and the outlet port 243 is through channels 245 and 246 of a valve chamber plug 241, a valve chamber 248 and a channel 249. This passage, however, is normally closed by a valve head 250 which is normally pressed against a valve seat 25| by a spring 252. Meanwhile, the cap 240, which comprises a valve head upon the opposite end of a valve stem 253, is maintained unseated from a seat 254 in the exhaust line which includes an axial channel 255, a transverse channel 256 and a chamber wall channel 251 leading to the exhaust port 244. When the valvecap 240 is pressed to the left, as viewed in Fig. 6, it will press against the seat 254 to terminate communication between the outlet port 243 and the exhaust port 244 while unseating the valve head 250 from the seat 25| and thus providing communication between the inlet port 242 and said outlet port 243.

The governor or speed-responsive apparatus `for controlling the movement of the link 239 includes a cylindrical housing 260 of which a hub 26| is splined to a section 262 of the transmissicnmainshaft 2|. Fulcrum members in the form of studs .263 for inertia weights 264 are anchored to the web of said housing 260, pivot pins 265 being carried by said studs for the pivotal support of said inertia weights. Heel portions 266 upon the weights 264, when these weights are pivoted about the pins 265 by centrifugal action, bear against a collar 261 for shifting the same to the left together with a sleeve 268 and a collar engage the ends of legs 213 of a fork 214', cause this fork and the shaft 215 upon which it is fixedly mounted to rotate clockwise, thereby causing clockwise rotation of an arm 216, which is attached to the lower end of the shaft 215 Iexteriorly of the casing 211, against the force of a spring 219 which constantly urges the weights 264 inwardly in opposition to their centrifugal force. Thus the link 239 which is pivotally connected to the arm 216 by pin 218 is moved to the right for actuating the valves 2|1 and 236 as above described.

Detent means I(not shown) of any conventional structure is employed in association with the inertia weights 264 to prevent their movement 'from the low speed position in which they are shown until a selected minimum critical speed is attained by the shaft 2|, at which time they will quickly pivot clockwise to a higher speed position. Similar detent means (not shown) is provided in association with these weights for retaining them in the clockwise position until the speed of said shaft 2| is reduced to a predetermined minimum. In this manner the weights 264 are caused to move quickly between the extremities of their oscillative movement.

It will be recalled that the valve 2|1, when actuated by the speed-responsive device |86, is conditioned for terminating the communication of the reservoir 2|4 with the cylinder 206 of the fluid motor 205, and for connecting said cylinder with the exhaust port 233 of said valve so the pressure in said cylinder will be relieved and the spring 209 will become effective for shifting the link 2|0 in the direction to cause counter-clockwise rotation of the cam plate |18, Fig. 2, to place the short radius profile section |83 thereof in registry with the roller |84, thereby leaving the second and third speed power trains untrammelled for automatic mobilization so far as this part of the control apparatus is concerned. The valve 236, however, in cooperation with a switching valve 280 (shown schematically in Fig. 1 and in detail in Fig. 8) and a throttle-responsive valve 28| (shown schematically in Fig. 1 and in detail in Fig. 5) serves to control inflation of the clutch envelope 3| and hence the degree of resistance to relative rotation between the driving and driven parts of the main clutch C. An interlock between the engine throttle and the throttle-responsive valve 28| is provided by an accelerator pedal 282 which is shown in association with said valve 28| in both Figs. 1 and 5.

Before describing these additional valves in detail, their relation to each other and their general environment in the pressure-fluid control system will be made clear. In the operation of the valves 236, 280 and 28|, pressurefluid, impressed from the reservoir 2| 4 through -conduits 2|5 and 284 upon the valve 28| is metered throughsuch valve into a conduit 285 and thence through valve 280, conduit 59, the tting 55, tube 31 in the transmission mainshaft 2|, pasages 36 and 4|, tube 35 and into the envelope 3| for creating a pressure in the envelope of a magnitude corresponding to the degree of throttle opening, or, the degreel to which the accelerator pedal 282 is depressed. Hence in starting the vehicle from rest, pressure-iluld from the reservoir 2|4 will be introduced into .link 239 to the right in Fig. 1 for manipulating the valve 236 whereby the pressure-huid carried to the intake port 242 'of this valve through the conduit 2|5 will be passed through the valve and outwardly of its outlet port 243 through the conduit 283 and through the valve 280 (which will be actuated by the predominant pressure of the fluid introduced through the conduit 283 for connecting the conduit 283 with the conduit 59 and disconnecting the conduit 285 from said conduit 59), the conduit 59' and theabove traced fluid line to the envelope 3| for imposing the full pressure of fluid from the reservoir 2|4 upon the clutch C to maintain. the same cornpletely engaged. lThis action of the valves 236,

. 280 and 28| will be fully understood after the valves 280 and 28| have been described in detail.

In Fig. 8 the switching valve 280 will be seen to comprise a cylinder 290 having one inlet port 292 'connected with the conduit 283 and a second inlet port 293 connected with the conduit 285. An outlet port 294 of this valve is connected with the conduit 59. It will be understood that when pressure-fluid is introduced either of the inlet ports 292 or 293 the force of that iiuid will cause a piston 29| to shift to the opposite end of the cylinder 290 and thus provide communication between the inlet port at which the pressure-Huid is introduced and the voutlet port 294. If pressure-fluid-is supplied toboth of the inlet ports 292 and 293 the piston 29| will be forced to the end of the cylinder at which the fluid pressure is least, thereby connecting the port having iluid at the greatest pressure with the outlet port 294 and disconnecting the inlet port of least pressure from the outlet port.

The accelerator-operated valve 28|, Fig. 5, is associated with the foot accelerator pedal 282 which is pivotally connected at its lower end into Fluid introduced into the inlet por-t ana and through a iilter member 3|3 in "an entrance cavity 3| 4 is withheld from further ingress into the cevice through a passage 3|5 by a valve ball 3|6 so long as the accelerator pedal 282 is in its upper or released position as shown, but when said pedal is vpressed downwardly by the t foot of the operator to open the engine throttle,

' is hermetically sealed about its circular edge be- `the ball -3I6 will be moved downwardly, as

presently explained, from the end ofthe passage 3|5 for a suilicientlength of time to admit fluid upwardly through said passage and outwardly of the port 309 untila back pressure is built up in the channel 3|9 corresponding to the amount of throttle opening. When the accelerator pedal 282 is released, communication is established between the outlet port 309 and the exhaust port 3|2 through the passage 3|9 and an exhaust tube 320.

The valve 28| is divided into upper and lower sections by ailexible metal diaphragm 32| which tween casing parts 303 and 323. The diaphragm 32| receives the tube 320 in a central opening and a Yspring seat 324 and a ange 325 upon the exhaust tube 320. hermetically clamp thecentral section of the diaphragm 32| therebetween. A spring 32B bearing against the lower edge of the ange 325 constantly urges the diaphragm 32| with a pivot rod t300. which is mounted in a bracket A30| upon a plate 302 secured to the upper end of the casing 303 of .said valve by a plurality of screws as 304. A spring 305 which is wrapped about the rod 300 has an end section 308 which in zits uppermost' position, as shown in Fig. 5. A linkage (not shown) 'for operably connecting the pedal 282 with the vehicle throttle valve is connectible with said pedal at an apertured lug 301. Said pedal carries a roller 301a for actuating the valve 28| by pressing downwardly upon a button 301b of the valve when the pedal is depressed in the conventional manner Tor opening the vehicle throttle.`

Pressure-fluid is admitted into Vthe valve through the conduit 284, Fig. 1, which is connected with the inlet port 308 and an outlet port for the pressure-fluid is provided at 309 where the conduit 285 is attached.l A second outlet port 3l'0, not used in the present-installation, is closed ,by a screw plug 3| An exhaust port 3|2 is also provided in the side wall of the valve casing.

upwardly as well as the spring seat 324 and a tubular spring guide 321 'which is threaded .onto the tube 320. A pressure graduating spring 328 surrounds the tubular guide 321 and is held selec-A tively compressed between the seat 324 and a seat member 329 at the upper end of said spring, said .seat member 329 bearing against a shoulder '330 within a hollow piston member 33| whichis vertically reciprocal in the cylindrical casing 303.

While the pedal 282 is in the released position as shown, the spring 326 will be effective for maintaining the diaphragm 32| in the upward position illustrated as well as the graduating spring assembly comprising the graduating spring328, the spring guide 321 and the exhaust tube 320. Upon depressing the accelerator pedal the roller 301e will be-caused to bear against the button 30117 to force the piston `33| and the said graduating spring assembly downwardly. Pursuarrt to this downward movementof the graduated spring assembly avseat 332 at thelower' end of the `exhaust tube 320 will be pressed against an exhaust ball 333 of an intake and exhaust f upon the ball 3|6 for holding it in closing relav tion with the passage 3|5. Additional downward movement of the accelerator pedal 282 will, however, through the spring 328, force the diaphragm 32|, the tube 320 andthe intake and exhaust assembly 324 downwardly for unseating the ball 3|8 from the passage 3|5. Resistance to this downward movement is encountered because of force of the pressure-fluid upon the ball 3| 6 wherefore the graduating spring 328 will be slightly compressed incident to the flange or collar 329 sliding downwardly along the spring 15 guide 321. The fluid thus admitted through the This pressing of the *seatA l passage 3|8 and the channel 3|8, and hence into the envelope 3| of the clutch C, will also pass through one or more openings 348 into the chamber 84| below the diaphragm 32| and thus augment the force of the spring 328 in urging the diaphragm upwardly at its center. Eventually the pressure of iluid in the channel 3| 8 and in the chamber 34| will reach a magnitude suilicient for lifting the diaphragm 32| against the force of the graduating spring 328 and when this happens the spring 338 will cause the balls 333 and 3|8 to follow the tube 328 upwardly, whereby the exhaust passage remains closed at the seat 332 to maintain the pressure in the channel 3| 8. When the ball 3| 8 reaches closing relation with the lower end of pmsage 3|5 no more fluid will be admitted to the channel 3|9, and so long as the accelerator pedal 282 remains undisturbed, the pressure in the channel 3|9 will remain fixed.

Upon further depressing the accelerator pedal the piston 33| and the upper end of the graduating spring 328 will be shifted downwardly incident to further compressing the spring 328 while moving its lower end and the center of the diaphragm 32| downwardly to cause downward movement of the tube 328 and the valve balls 333 and 3| 8. Thus additional pressure-iiuid is admitted through the passage 3|5 into the channel 3|8, and when enough iluid has been admitted into said channel and through the opening 340 into the chamber 34|, the diaphragm 32| will again be lifted at its center while still further compressing the graduating spring 328. When the graduating spring is compressed enough to have permitted upward movement of the tube 320 and the balls 333 and 3|8 suillciently for the ball 3|8 to have again closed the passage 3|8, the pressure in the passage 3|! will remain fixed at the higher value so long as the pedal 282 remains unmoved.

Upon any further depression of the accelerator pedal and the consequent increment in the compression of the graduating'spring 328, a corresponding increase in pressure will be incurred in the channel 3|9 by fluid admitted through the passage 3|5, for when the depression of the accelerator pedal is stopped at any given point, the iluid admitted from the cavity 3|4 through the passage 3|5 and the hole 340 will quickly lift the diaphragm 32| suiliciently to permit the spring 338 to close the passage 3|5 with the ball 3|8 and thus strike a balance where the pressure in the channel 3| 9 corresponds to the degree of advancement of said accelerator pedal.

Upon partial release of the accelerator pedal after a pressure has been built up in the channel 3|8, the tension in the graduating spring 328 will be partially relieved by a, slight upward movement of its upper end with the piston 33| and the collar 329 relatively to the guide 321, and as a consequence of this, the pressure in the channel 3|8 and in the chamber 34| will be effective for moving the diaphragm 32| upwardly to unseat the lower end of the tube 320 from the exhaust ball 333, thus permitting escape of pressure-iluid through the tube 320, apertures 331, the interior of the valve casing 303 and the exhaust port 3|2. When the pressure in the channel 3|9 decreases sufilciently the compressed graduating spring 328 will be effective for forcing its lower end and the diaphragm 32| downwardly far enough to cause reengagement of the seat 332 with the exhaust ball 333. The pressure within the channel 3 8 may be further decreased by an amount determined by an additional partial release of the foot accelerator pedal for further diminishing the tension in the graduating Spring 328, there being a repetition of the action of the pressure within the chamber 34| nrst lifting the diaphragm 32| to unseat the exhaust seat 332 and the compressed spring 328 thereafter being effective for forcing the diaphragm 32| downwardly as the pressure in the chamber 34| decreases with the escape of pressure-fluid into the exhaust passage, until finally a balance is reached concurrently with the seat 332 reaching the exhaust ball 333.

It will be seen from the foregoing description that the valve 28| is effective for maintaining a pressure in the channel 3|8 proportional to the degree of depression of the accelerator pedal 282.

Operation of the apparatus:

In starting a vehicle, upon which the present apparatus is installed, from rest, a manual control (not shown) will be manipulated by the operator for rotating the arm |85, Fig. 3, and the shaft |84 upon which it is mounted for rotating the cam plate |83, Figs. 2 and 3, either clockwise or counter-clockwise 'from the neutral position shown in Fig. 2. If it is desired to move forwardly the cam -plate |83 will be rotated counter-clockwise whereby the stud will be cammed to the right by the edge |89 `of the ,slot |82. In this manner the shifter fork |52 and the clutch ring '|2, Figs. l and 2, will be moved to the right for meshing the clutch teeth 13 and 15', thus mobilizing the rst speed power train. This having been done the operator will accelerate the vehicle engine by depressing the accelerator pedal 282 and concurrently the roller 30111 upon said pedal will be brought into vengagement with the button 3011 of the valve 28| and the valve actuated in the manner hereinabove described for admitting pressure-fluid from the reservoir 2|4 and the conduit 284 into the channel 3|9 of said valve and hence through the conduit 285 into the right end of the switching valve 280, Figs. 1 and 8. At this time the transmission mainshaft 2| will be at rest wherefore the speed-responsive device |88 will be in its inactive position as shown in Fig. 1 and the valve 238 will be conditioned for stopping the flow of pressure-fluid thercinto through the conduit 2|5 and for connecting the conduit 283 and hence the left end of the switching valve 280 with the exhaust port 244 of said valve 238. Since the left end of the switching valve 288 is then connected with an exhaust, the pressure-fluid introduced into the right end of this valve member will throw the piston 29| to the left for cutting ol communication between the conduit 283 and either of the conduits 285 or 59 and for establishing communication between the conduits 285 and 59. Since the conduit 59 constitutes a section of the line through which pressure-iluid is carried for admittance into the clutch envelope 3|, the pressure in this line and in the envelope 3| will reach amounts depending upon the amount of advancement of the pedal 282. The valve 28| will be so regulated that the degree of inflation of the envelope 3| will be such, with respect to the advancement of the accelerator pedal, that the clutch will transmit power from the engine to the transmission mainshaft 2| in a sufilcient amount to prevent engine rush but to provide for adequate engine speed for developing sulllcient power for driving the mainshaft and the vehicle load with which it is connected. As the pedal 282 is advanced and the vehicle engine throttle opened the clutch C will thus uniformly engage the driven friction elements 33 with the clutch driving member l1, the

. power being transmitted through the shaft extension 20 and the mainshaft 2|, gears 61 and 68, clutch teeth 13' and 15', the ovlerrunning clutch 11, gear 19, countershaft |4, bevel gears and I6 and outwardly of the device through a driven shaft 2 to the vehicle running gear.

After the clutch C is fully engaged lso there is no slippage between the friction elements upon its driving and driven parts and after the vehicle and the vehicle engine have attained a predetermined minimum speed, the speed-responsive device |86 will become effective in the manner hereinabove described for shifting the link 239, Fig. 1, to the right for actuating the valves 2|1 and 238 by pressing their valve stem caps 235 and 240 inwardly thereof.

Upon this manipulation of the valve 236 the conduit 283 will be disconnected from communication with the valve exhaust port 244 and will be connected with the reservoir 2| 4 through the inlet port 242 of said valve and the conduit 2|5. In this. manner the full force of the pressurefluid in the reservoir 2|4 is impressed upon the left end of the piston 29| in the switching valve 280 to force this piston to the right end of the valve upon release of the accelerator pedal 282 and the concomitant adjustment of the throttlecontrolled valve 28| for connecting the conduit 285 and the right end of the valve 280 with they exhaust port 3|2 of said valve 28|. Subsequent depression and release of the pedal 28| during operation of the vehicle will be ineffective for shifting the piston 29| tothe left since the pressure in the conduit 285 will never exceed that Vin the reservoir 2|4 which reservoir pressure is supplied in the left end of the valve. Therefore, after the transmission mainshaft 2| attains the speed at which the inertia weights 264 are thrown outwardly, the valves 236 and 280 will function for directing pressure-fluid into the conduit 59 independently of the throttle-responsive valve 28| and to maintain the clutch C fully engaged irrespective of the position of the accelerator pedal.

It will be noted, however, that each time the accelerator pedal is depressed, iiuid from the reservoir 2|4 will be admitted into the valve channel 3 I 9 and into the conduit 285, the amount of fluid and the pressure thereof depending on the amount of the advancement of the pedal, and that upon release of the accelerator pedal the seat 332 at the bottom of the exhaust tube 320 will be lifted from the exhaust ball 333 to result in the exhausting of fluid from the conduit 285 and the channel 3|9. Consequently, in

-order to conserve pressure-fluid, which in the present installation is compressed air that is exhausted to the atmosphere through the exther conditioned for connecting the conduit 208 with the exhaust port 233 of said valve whereby the springin the motor 205 becomes operable to force the piston to the opposite extremity oi' its reciprocal movement while expelling fthe fluid outwardly through the conduit 208 and the exhaust port 233. Thismovement of the piston pulls the rod 2|0 with it to cause counter-clockwise rotation of the arm |11, Fig. 4, and of the sleeve |15,Fig. 2, with which said arm ls connected. Thus the cam plate |18, Fig. 2, which is connected with the sleeve |15 is rotated counter-clockwise to carry the short radius profile |83 thereof into registry with the roller |84. When thus positioned, the cam plate |18 will -permit the arm |86 carrying the roller |84 to pivot clockwise about its pivot-pin |98 and thus permit the link |96 and the adjacent ends of the haust passage 3|2, the switching valve 280 will be b placed closely to the throttle-responsive valve 28| to shorten the conduit 285 and minimize the volumetric capacity of this conduit.

It will be understood from the above detailed description of the valve 2|1 that upon attainment of said predetermined speed of the mainshaft 2| and the `actuation of the speed-responsive device |86 for pressing the stem of said valve inwardly, said valve will be conditioned for terminating the communication between the inlet port 222 and the conduit 208 whereby pressure-fluid is no longer available through the conduits 2|5, 2|6, said valve 2|1 and the conduit 208 for maintaining the piston of the fluid motor 205 at the extremity of reciprocal movement illustrated in Fig. 4. Said valve 2 |1 is furarms |95 and 203 to move toward the cam plate |18 in the direction they are urged by the springs and 200. This action occurs upon said counter-clockwise rotation of the cam plate |18 since the cam plate |63 was previously rotated counter-clockwise, While mobilizing the first speed power train, to carry its short radius profile |83 into registry withythe roller |84. The springs |90 and 200, in addition to rotating the arms and 203 also rotate the shifter forks |34 and ||1 respectively counter-clockwise and clockwise as viewed in Fig. 2 to carry the teeth 84 of the second speed jaw clutch |09 against the teeh 85 of that clutch and to similarly carry the teeth ||2 of the third speed jaw clutch 3 into engagement with the teeth thereof.

At this time, while the apparatus is operating in the flrst speed power train, the transmission mainshaft 2| will be rotating at greater speed than the second and third speed gears 86 or ||0 and consequently the teeth of the clutches |09 and ||3 will not mesh. The faces 81 of the teeth 84 will simply ratchet over the teeth 85 and likewise the faces ||2' of the teeth ||2 will simply ratchet over the ends of the teeth While the vehicle is thus proceeding forwardly with the first speed power train in operation and at any time following the critical minimum speed at which the speed-responsive device |86 operates for indirectly causing counter-clockwise rotation of the cam plate |18, the operator may change over into the second speed power train by releasing the accelerator pedal to permit the vehicle engine and the transmission mainshaft 2| to decelerate suiliciently to cause the clutch teeth 84 of the second speed jaw clutch |09 to synchronize with the teeth 85, of said clutch whereupon the spring |90 will be effective for causing the teeth 84 to slide into mesh with said teeth 85. Meanwhile, the gear 86 which carries the clutch teeth 85, due to the momentum of the vehicle running gear with which it is connected through the countershaft I 4, will have maintained substantially a constant speed of rotation. This connection with the countershaft is mpositive in character, it being due to the frictional drag of the overrunning clutch 93, of the bearing 90,

' of a thrust ring R carried on said countershaft and frictionally engaging the back end of the gear 89. Likewise, the gear 19, which is splined to the countershaft I4, will have maintained substantially a constant rate of rotation, but that part of the first speed power train including the gears 61, 68, the clutch teeth 13 and 15', and

the driving member 16 of the first speed overrunning clutch 11 will have decelerated with the vehicle engine as permitted by the clutch rollers 82. When the second speed jaw clutch |08 is engaged the second speed power train will be established and will enable the engine to pick up the load upon depression of the accelerator pedal 282. The gear 18 will continue to overrun the driving member 16 of the first speed overrunning clutch 11 when its ange 85 is connected in series with the gears 86 and 89 and the overrunning clutch 83 as part of the second speed power train.

When it is desired to change over into the third speed power train the operator will again release the accelerator pedal 282 for closing the engine throttle and decelerating the engine together with the transmission mainshaft 2| and the third speed jaw clutch teeth ||2 which rotate with said shaft 2|. Concurrently the momentum of the vehicle will keep the countershaft I4 and the gear 18 keyed thereto rotating at substantially constant speed as permitted by the overrunning clutch rollers 82 and 84, and when the clutch teeth ||2 slow down to synchronisrn with the clutch teeth III, which had been rotating at slower speed than the clutch teeth 2 because of the connection with the countershaft I4 through the gears |20 and ||0, the spring 200 will be effective for sliding said teeth ||2 into mesh with the teeth I I I for establishing the third speed power train. Subsequent depression of the accelerator pedal 282 will cause power from the engine to be transmitted through the third speed power train comprising the jaw clutch ||3 and the gears and |20. Meanwhile, the driven parts of the overrunning clutches 11 and 93 respectively of the rst and second speed power trains and carried upon the gear 19 will be rotating at a speed in excess of the driving mem-bers 16 and 92 of these clutches as permitted by the clutch rollers 82 and 94.

If at any time the operator should care to change over from the third speed power train to the second speed power train as he may want to do in order to obtain greater accelerating power for passing another vehicle upon the highway, he may accomplish this act by causing counter-clockwise rotation of a cam 350, Fig. 2, which is rotatively supported upon a stud 35| in the upper wall of the gear box. This rotation of the cam 350 will carry a long radius profile section 352 thereof against a roller 353 upon an arm 354 which is pivoted upon a pin 355 in the upper side wall of the gear box. A spring 356 wound about the hub 351 of the arm 354 has an end section 358 bent into the form of a hook and constantly bearing against said arm for pressing the roller 353 against the profile of the cam 350. When the cam section 352 is brought against the roller 353 the arm 354 will be pivoted clockwise for causing endwise movement of a link 358 which has an end connected with the free end of the arm 354 by a pin 360 and which has at its opposite end a pin 36| projecting into an elongated slot 362 in the arm 203. While the apparatus is connected in the third speed power train the arm 203 will be rotated clockwise with the shifter fork I I1 so that the counter-clockwise end of the slot 362, with respect to the axis in the shifter fork shaft ||8, will be in receiving relation with the pin 36| so that when the link 358 is moved endwise as stated above, the pin 36| will bear against said counter-clockwise end of the slot 362 for pivoting the arm 203 and hence shifter fork I I1 counter-clockwise into the position shown for disengaging the third speed jaw clutch I I3. With the third speed power train thus demobilized, the

' vehicle engine will speed up for picking up the load through the second speed power train which includes the overrunning clutch 83.

Said counter-clockwise rotation of the cam 35| for disengaging the third speed jaw clutch III also carried said profile section 352 from registry with a roller 363, Fig. 2, which is mounted upon a base extension section 363 of the shifter fork |0I, and carried a short radius profile section 364 into registry with such roller to permit sliding movement of said shifter fork to the left upon the shifter fork rod |41 under the inuence of a compressed spring 365 which is disposed about said rod |41 with its opposite ends respectively bearing against the right end wall of the gear box and the base of said shifter fork. Therefore, when the engine is speeded up sufficiently for picking up the load through the second speed power train incident to bringing the driving member 82 of the second speed overrunning clutch 33 up to the speed of the flange 85 upon the gear 19, the clutch teeth |02 and |03 of the lockout clutch 31 will be brought into synchronism so the movement of the shifter fork |0| to the left in the manner described by the force exerted by the spring 365 will result in the meshing of the clutch teeth |02 with the teeth |03 to lock out the overrunning clutch 83 and thus convert the second speed power train into a two-way-drive power train.

Rotation of the cam 350 is eiected by the operator manipulating valve means (not shown). which may be similar to the valve 236 in Fig. 1, for establishing communication of a conduit 310,

y Fig. 2, with a fluid pressure source to force a piston (not shown) in a cylinder section 31| oi a fluid motor 312 to the left incident to compressing a spring (not shown) in a spring'chamber 313 of said motor and moving a rod. 314 connected with said piston to the left. Said piston rod 314 is operably connected with said cam through an arm 315 which is also rotatable upon the stud 35|.

When it is again desired to establish the third speed power train, the operator will relieve the fluid pressure extended through the conduit 310 to the fluid motor 312 whereby said spring (not shown) within the spring chamber 313 will retract said piston (not shown), the piston rod 314 and the arm 315 to cause clockwise rotation of the cam 350 into the position shown. The roller 363 is thus cammed radially outwardly onto the long radius section 352 for disengaging the clutch 91 and for carrying the short radius section of said cam into registry with the roller 353 to enable the spring 200 to again rotate the shifter fork I|1 for pressing the clutch teeth I|2 against the clutch teeth By thereafter decelerating the vehicle engine as hereinabove described the clutch teeth ||2 may be slowed down to synchronism with the clutch teeth I I I and permitted to mesh therewith.

When the reverse power train is established as above described by rotating the cam plate |63 clockwise as viewed in Fig. 2 for shifting the reverse idler gear |3| mutually into mesh with the gears |30 and 19, the vehicle will be started rearwardly by simply pressing upon the accelerator pedal 282 for feeding fuel to the engine and opening the Valve 28| for admitting pressure-huid from the reservoir 2|4 through the switching valve 280 and the pressure line including the conduit 58 to the clutch envelope 3|. As before, the inflation of the envelope and the pressure between the friction elements upon the driving and 1l driven members of the clutch will be controlled in In bringing the vehicle to a stop the operator need use only his brake, for after the speed-res sponsive device slows down sufilciently the weights 264 will permit the spring 219 to pivot the arm 210 for moving the link 239 to the left and permitting outward movement of the valve stems of the valvesf2|`| and 230. Valve 2|'I will then re-connect the motor 205 with the pressurefluid source so this motor will rotate the cam |18 for placing its long radius proille section |8| in registry with the roller' |84 whereby the arms |05. |90, and 203 are rotated to disengage the third and secondspeed jaw clutches ||3 and |09. The first speed power train remains mobilized but when the stem ofl valve 236 moves outwardly the direct connection through this valve of the reservoir 2H with the clutch'envelope 3| is terminated so that the engagement of clutch C will depend upon whether the accelerator pedal is depressed. Consequently the mobilized first speed power train is disconnected from the engine when the operator releases the accelerator pedal as the brakes are applied for stopping.

'I'he performance of the clutch C is analogous to that of a fluid flywheel insofar as it automatically Iprovides uniformly diminishing slippage for a smooth initial engagement and absorbs tortional vibrations originating in the engine. It has the additional advantage, however, of dispensing with' the continual slippage that occurs in the fluid flywheel type of clutch.

This improved clutch installation is made practical by virtue of the combination therewith of the pressure-fluid control system therefor interlocked for operation in accordance with the amount of throttle opening and engine and vehicular speed, and also by virtue of the automatic change-speed apparatus which eifects changes in speed ratio without incurring disengagement and reengagement of said clutch.

Since all power trains inr theA present transmission include paired gears respectively upon the mainshaft and the countershaft, the layout has been designed to minimize vibration by arranging the gears of the higher ratio trains,

which are used for greater time periods and for transmitting the most power, adjacently to the bearings which support these shafts in opposite end walls of the gear box. l

Attention is also particularly directed kto the control feature of the transmission that provides for conditioning the lock-out jaw clutch for the second speed overrunning clutch whereby said overrunning clutch is automatically shunted out to convert the second speed power train into a two-way-drive train when the manually supervised shift is made to this train from the third speed power train. This \method of control simplifies the shifting operation and thus avoids any likelihood of the operator becoming confused when shifting from third to second speed to employ the braking force of the engine while descending a steep grade.

I claim:

1. In a system wherein a power transmission mechanism is employed for transmitting power between driving and driven shafts. and wherein said transmission mechanism comprises a plurality of power trains of graduated speed attaining capabilities successively and automatically establishable in driving relation between said shafts, the combination oi' cam means having disposable in an active position relatively to a higher speed one of said trains to preclude its establishment between said shafts and retractable into an inactive position with respect to said 'higher speedtrain to leave it free for automatic establishment, a clutch engageable to condition a lower speed train of said trains for operation, means manually settable to concurrently engage said clutch and to retract one of said cam parts from its active position, means yieldingly urging the other of said cam parts into the inactive position, and a fluid motor connected with said other cam part and energizable only when subjectedto a differential of pressure-fluid to disposethe same in the active position.

2. In a system wherein a power transmission mechanism is employed for transmitting power between driving and driven shafts, and wherein said transmission mechanism comprises a plurality of power trains of graduated speed transmitting capabilities successively and automatically establishable in driving relation between said shafts, the combination of cam means associated with and disposable in an active'position relatively to a higher speed train of said power trains to preclude its establishment between said shafts and retractable into an inactive position with respect to said higher speed power train to leave itfree for automatic establishment, a fluid pressure responsive unit operably connected with said cam means, said unit being operableA for placing said cam means either in the active po- .sition or inthe inactive position according to whether a section of said unit is subjected to atmospheric pressure or to a pressure differing from atmospheric pressure, a source of fluid at pressure differing from atmospheric pressure, and means responsive to the speed of one of said shafts and operable to alternatively subject said unit to the pressure of said fluid source or to atmospheric pressure according to whether speeds above or below a predetermined speed are recorded. y

3. In a transmission having a plurality of power trains of graduated speed transmitting capabilities for establishing a one-way driving -connection between driving and driven members and having means for automatically establishing a next higher speed train in response to a drop in driving member speed, means for initially establishing a low speed train, control means for positively maintaining the means for automatically establishing the higher speed trains inactive at selected low speeds of the driven member, and means responsive to a selected speed of one of said members when the latter is accelerating for nullifying the action of said control means so it no longer maintains the higher speed establishing means inactive.

4. In a transmission having a plurality of power trains of graduated speed transmitting capabilities for establishing a one-way driving connection between driving and driven members and having means for automatically establishing a next higher speed train in response to a drop in driving member speed, manually functioned means for initially establishing a low speed train, fluid pressure means for positively maintaining the means for automatically establishing the higher speed trains inactive at selected low speeds of the driven member and means responsive to a selected speed of one of said members when the latter is accelerating for rendering the uid pressure means inoperable, whereby the means for separately operable parts associated with and I0 automatically establishing the higher Speed ratios in the transmission is conditioned for functioning.

5. In a transmission having a low-speed train and at least one higher speed train for establishing a driving connection between driving l and driven members and having means for automatically establishing the higher speed train in response to a drop in driving member speed, a clutch normally urged to establish a connection through the higher speed train between the driving and driven members, means terminating in a cam follower for controlling the engagement or disengagement of said clutch, a pair of aligned cams each having a profile of which both are engaged by said follower and each profile having a first portion for registering with the follower so as to permit closing of the clutch and a second portion registerable with the follower so as to open the clutch, manual means for operating one cam to place its first prole portion in registry with the follower while concurrently connecting the driving and driven members through the low speed ratio, and means responsive to a selected speed of one of said members when the latter is accelerating for operating the second cam so as to place its rst profile portion in registry with the follower and thereby to condition the transmission for establishing the higher speed train.

6. 1n a transmission having a low-speed train and at least one higher speed train for establishing a driving connection between driving and driven members and having means for automatically establishing the higher speed train in response to a drop in driving member speed, a clutch inthe higher speed train of the type wherein the two clutching members may be urged into engagement without damaging them, and yet without engaging them until the two parts reach a common speed, means for urging the two parts of the clutch into engagement, means terminating in a cam follower for controlling the engagement or disengagement of said clutch, a pair of aligned cams having respective profiles both cooperable with said follower and each prole having a first portion registerable with the follower to avoid interference with closing of the clutch and a second portion registerable with the follower to move the same into position for holding the clutch open, manual means for operating one of said cams to place its rst prole portion in registry with the follower so that it will permit closing the clutch while concurrently connecting the driving and driven members through the lowspeed train, and means responsive to a selected speed of one of said members when the latter is accelerating for operating the second cam to carry its rst prole portion into registry with said follower so as to permit closing of the clutch and thereby condition the transmission for establishing higher speed train.

7. In a transmission having a low-speed train and at least two higher speed trains for establishing driving connections between driving and driven members and having means for automatically individually establishing said higher speed trains in response to a drop in driving member speed, a clutch in each of the higher speed trains normally urged to establish a connection therethrough between the driving and driven members, linkage means terminating in a cam follower for controlling the engagement or disengagement of both of said clutches, a pair of aligned cams having profiles of which both are cooperable with said follower and each profile having a first portion registerable with the follower so as to avoid interference with closing of the clutches and a second portion registerable with the follower to hold the same for opening said clutches, manual means for operating one of said cams to place its first profile portion in registry with the follower to permit closing both clutches while concurrently connecting the driving and driven members through the low speed ratio, and means responsive to a selected increased speed of one of said members for operating the other cam to place its rst profile portion in registry with the follower to permit closing of both of said clutches and thereby to condition the transmission for establishing the higher speed trains pursuant to the functioning of the means for automatically establishing said trains.

8. In a transmission having a low speed train and at least two higher speed trains for establishing a one-way driving connection between driving and driven members and having means for automatically individually establishing the higher speed trains in response to a drop in driving member speed, means for initially establishing a low speed train, means for positively maintaining the means for automatically establishing the higher speed trains inactive at'selected low speeds of one of said members and responsive to a higher speed of said one member for rendering operative the means for automatically establishing the higher speed trains, and manual means operable at will for establishing a. lower speed train while the automatic means has the transmission connected through a ihigher speed train.

OSCAR H. BANKER.

REFERENCES CITED The following references are of record in the le of this lpatent:

UNITED STATES PATENTS Number Name Date 1,985,884 Banker Jan. 1, 1935 2,120,104 Livermore June 7, 1938 2,140,502 Banker Dec. 20, 1938 2,177,904 Maybach Oct. 31, 1939 2,203,296 Fleischel June 4, 1940 2,262,747 Banker Nov. 18, 1941 

